EP2620715A1 - Procédé de fonctionnement d'un appareil de chauffage et d'aération et appareil de chauffage et d'aération - Google Patents

Procédé de fonctionnement d'un appareil de chauffage et d'aération et appareil de chauffage et d'aération Download PDF

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Publication number
EP2620715A1
EP2620715A1 EP12000489.0A EP12000489A EP2620715A1 EP 2620715 A1 EP2620715 A1 EP 2620715A1 EP 12000489 A EP12000489 A EP 12000489A EP 2620715 A1 EP2620715 A1 EP 2620715A1
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EP
European Patent Office
Prior art keywords
air
temperature
refrigerant
heat exchanger
heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12000489.0A
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German (de)
English (en)
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EP2620715B1 (fr
Inventor
Johannes Dr. Brugmann
Kai Dr. Schiefelbein
Fabien Beber
Michael Schaumlöffel
Enno Wagner
Lutz Grünig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Stiebel Eltron GmbH and Co KG
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Stiebel Eltron GmbH and Co KG
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Priority to EP12000489.0A priority Critical patent/EP2620715B1/fr
Publication of EP2620715A1 publication Critical patent/EP2620715A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
    • F24F12/003—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid using a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/006—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an air-to-air heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0096—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater combined with domestic apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/56—Heat recovery units

Definitions

  • the invention relates to a method for operating a ventilation heater with heat recovery.
  • Outside air is passed through an air / air heat exchanger and absorbs heat from an exhaust air in the air / air heat exchanger.
  • Exhaust air is passed in the flow direction from the air / air heat exchanger coming as a heat source to an evaporator of a heat pump to evaporate a refrigerant contained in a refrigerant circuit.
  • To the exhaust air outside air can be mixed for a sufficient energy content.
  • the invention relates to a ventilation heater with an air / air heat exchanger for the transmission of heat energy from an exhaust air from heated spaces to an outside air stream with a arranged in a heat pump in a refrigerant circuit evaporator, wherein the evaporator can be acted upon with an exhaust air stream from an exhaust duct.
  • An opening for outside air is provided in front of the evaporator, through which the outside air can be mixed into the exhaust air for a sufficient energy content as a heat source,
  • DE 10 2005 002 282 A1 is a ventilation system with a heat exchanger, which is acted upon by an outside air flow known.
  • the heat exchanger is an air / air heat exchanger in which an exhaust air flow from rooms to be heated transfers heat energy to the outside air flow.
  • the exhaust air leaving the heat exchanger transfers thermal energy to a refrigerant operated in the high-pressure range (WPKH) of the heat pump cycle (WPK) in the supercritical state.
  • WPKH high-pressure range
  • WPK heat pump cycle
  • a second heat exchanger 3 and / or heat exchanger 6 is provided in the heat pump circuit in addition to a heat exchanger for heating and / or cooling of the refrigerant.
  • the heat pump circuit WPK is designed for operation with a supercritical refrigerant.
  • Out DE 197 02 903 C2 is a multi-room air conditioning with a central heat pump comprising a central unit known.
  • a switchable refrigerant circuit of the heat pump and an air / refrigerant heat exchanger is provided to the exhaust air from the rooms and / or outside air can be fed.
  • a main heat exchanger is connected to the heating of rooms, and convectors are arranged in a first heating circuit with first circulation pump.
  • a secondary heat exchanger is arranged to heat a hot water tank in a second heating circuit.
  • the object of the invention is to heat a building in an efficient and cost-effective manner, in particular with heat recovery.
  • outside air is routed through an air / air heat exchanger.
  • the outside air absorbs heat from an exhaust air in the heat exchanger, and from the air / air heat exchanger Exhaust air is passed as a heat source to an evaporator of a heat pump.
  • a refrigerant contained in a refrigerant circuit is evaporated in the evaporator.
  • To the exhaust air can be added advantageously outside air for a sufficient energy content.
  • the supply air heated by the air / air heat exchanger with a first temperature T Ge of approximately 15-20 ° C. is heated in an air heater to a second temperature T Ga , and the second temperature T Ga is above a temperature t AB of the exhaust air.
  • CO 2 releases as a refrigerant in a supercritical state heat to the supply air, so that the supply air reaches the temperature T Ga .
  • the refrigerant is from a first state at a first temperature (t Üe ), which is supercritical, to a second state at a second temperature (t Üa ) at a near isobaric pressure, preferably between 73.8 and about 80 bar, cooled.
  • the CO 2 is further expanded before the evaporator through a throttle to a pressure below 73 bar.
  • the CO 2 flows in a flow direction at least partially counter to the flow direction of the supply air into the gas cooler of the air heater.
  • the CO 2 cools continuously in a temperature range between about 90 ° C and about 20 ° C, and the supply air is in the gas cooler in a temperature band with a lower first temperature value (t Ge ) of about 15 - about 20 ° C, in particular about 17-19 ° C, and an upper second temperature value (t Ga ) of about 25 - about 60 ° C, especially 30 - 50 ° C continuously heated.
  • the temperature curves of the warming supply air and the cooling CO 2 thus nestle against each other without abrupt temperature jumps or temperature ramps, and an increase in entropy and a loss of exergy are minimized during heat transfer.
  • the speed of at least one compressor of the refrigerant circuit is regulated for a continuous operation of the ventilation heater over a time interval of more than about 1 h without switching on and off.
  • the speed of the compressor is not tied to a constant temperature t Ga of the supply air and is dependent on a required value.
  • the speed in particular depends on a value of a power requirement, a high pressure of the heat pump or a Temperature regulated as the temperature t AU of the outside air or the temperature (t R ) of the room air.
  • the CO 2 in a refrigerant subcooler of an air preheater which is downstream of the gas cooler in the flow direction of the refrigerant and before the throttle, just as much enthalpy for subcooling the refrigerant before the air / air heat exchanger to the flowing outside air that at least freezing of the air / air heat exchanger is prevented.
  • the temperature (t AU ) of the outside air is a value with which the speed of the compressor is controlled so that the air / air heat exchanger does not freeze or, if so
  • the temperature (t AU ) of the outside air is brought behind the refrigerant subcooler to a temperature (t AU ) of at least -5 - +3 ° C.
  • a defrosting phase of the evaporator is initiated after the detection of an inadmissibly heavy icing of the evaporator.
  • a hot gas bypass defrost whereby the gas cooler is bypassed.
  • no refrigerant is passed through the gas cooler, whereby a cooling of the supply air is avoided during defrosting.
  • the ventilation through the air / air heat exchanger is advantageously carried out during defrosting, in particular with a smaller air volume flow than in heating operation.
  • at least one supply air fan or a fan which blows outside air through the air / air heat exchanger, throttled or stopped.
  • a sub-cooling of the refrigerant is also carried out during the hot water preparation.
  • the refrigerant is first supplied to the hot water heat exchanger and then flows into a refrigerant subcooler.
  • the refrigerant subcooler sits in the outside air flow in front of the air / air heat exchanger and serves to deliver at least as much heat to the outside air that the air / air heat exchanger just not iced.
  • the outside air is advantageously heated to a temperature of -5 to +3 ° C.
  • a ventilation heater is proposed with an air / air heat exchanger for the transmission of heat energy from an exhaust air flow from rooms to be heated to an outside air flow.
  • an evaporator is arranged in a refrigerant circuit. The evaporator can be acted upon by an exhaust air flow from an exhaust air duct.
  • an opening for outside air is advantageously provided in front of the evaporator, through which the outside air can be mixed into the exhaust air for a sufficient energy content as a heat source.
  • a gas cooler of the refrigerant circuit is further advantageously arranged in a supply air duct.
  • the gas cooler is arranged in the air flow direction of a supply air behind the air / air heat exchanger.
  • the outside air is advantageously sucked in accordance with a Venturi principle in the exhaust air flowing at a speed or also mixed by means of a fan of the exhaust air.
  • CO 2 is filled as a refrigerant, and heat is transferred in the heating mode of supercritical CO 2 as a refrigerant to the supply air behind the air / air heat exchanger.
  • the proportion of outside air is about 0- to 5-fold of the volume flow of the exhaust air, at an outside temperature of about 10 ° C advantageously about 0.5 times, at 0 ° C about 0.8 times and at - 10 ° C about 1 times the exhaust air.
  • the ventilation heater is characterized in that a refrigerant subcooler is arranged in the flow direction behind the gas cooler and in front of the throttle.
  • the refrigerant subcooler is advantageously arranged in the flow direction of the outside air in front of the air / air heat exchanger, and by emitting enthalpy, the supercritical CO 2 is undercooled, and a freezing of the air / air heat exchanger is prevented.
  • an enthalpy of about 0 to 50 kJ / kg is released from the refrigerant to the outside air, which heats up to about -5 to +3 ° C.
  • the outside air may well have temperatures of up to below -20 ° C, so that there is a temperature increase of up to 15 K or more.
  • a building is equipped with a corresponding ventilation heater and an air distribution system connected to the ventilation heater and heated with air.
  • the building advantageously has a specific value of the heat demand Q a of less than 20 kWh / m 2 per year.
  • the ventilation heater of the building advantageously has a specific heating power of about 5 to 20 W / m 2 , in particular 7 to 15 W / m 2 .
  • the ventilation heater has a heating power of 1500 W, with a corresponding passive house is preferably heated only with air.
  • the ventilation heater of the building has a thermal output which results from the multiplication of the living area m w of the building to be heated in square meters [m 2 ] with the specific value of the heat demand divided by a correction value K.
  • the correction value K is advantageously between 500 / a and 3000 / a, in particular between 1000 / a and 2000 / a and particularly advantageously between 1200 / a and 1500 / a. The result is still divided by 1000, which results in about the heating power of the ventilation heater in watts.
  • the correction value is also advantageous depending on the number of people or the hot water consumption of the building.
  • Ventilers with staged heating capacities are available.
  • a device is brought into the building, which advantageously has at least the required heating power.
  • a ventilation heater 1 has a refrigerant circuit 100 and at least one air / air heat exchanger 200.
  • a hot water tank 300 is also advantageously connected.
  • the refrigerant circuit 100 has a compressor 110, advantageously a three-way valve 120, an evaporator 160 and a throttle 150.
  • a gas cooler 170 is connected, which is located in an air heater 230.
  • the gas cooler 170 for air is connected to the refrigerant circuit 100 via a supply line 186 and a drain 187 for refrigerant.
  • either the gas cooler 170 for air or a gas cooler 130 for hot water preparation is integrated into the hot water tank 300 in the refrigerant circuit.
  • the gas cooler 130 for hot water is connected via a line 181 to the three-way valve 120. Furthermore, the hot water gas cooler 130 is connected to a refrigerant subcooler 140 via a conduit 182 in communication with a conduit 183. At a node 188, the drain 187 from the gas cooler 170 impinges air on the line 182, to which the gas cooler 130 for hot water is connected to the node 188.
  • the compressor 110 is connected via a line 180 to the three-way valve 120. Furthermore, the compressor 110 is connected via a line 185 to the evaporator 160. This evaporator 160 is in turn connected to the throttle 150, wherein the throttle in the flow direction c of the refrigerant upstream of the evaporator 160. Viewed in the flow direction c, the throttle 150 is located behind the refrigerant subcooler 140. The connection of the refrigerant subcooler 140 and the throttle 150 takes place with the line 184. Before the evaporator 160 of the refrigerant circuit 100, an opening 161 is provided, via which external air AU can be supplied to the evaporator 160 ,
  • the outside air AU is supplied to the refrigerant subcooler 140 at an outside air temperature t au .
  • the outside air AU flows through the refrigerant subcooler 140 and heats up.
  • the outside air AU then flows on to the air / air heat exchanger 200 via an outside air channel 280.
  • This air / air heat exchanger 200 is also supplied with exhaust air AB having an exhaust air temperature T AB via an exhaust air duct 210. With the exhaust air AB, the outside air AU is heated in a material separation. In the air / air heat exchanger 200, there is a heat transfer from the exhaust air AB to the outside air AU.
  • the thus heated outside air AU is conveyed by a supply air fan 221 through a supply air duct 220 and enters with a Temperature T Ga of the supply air ZU in the air heater 230 a.
  • the supply air is heated to ZU and continues to flow as supply air ZU via a supply air port 240 in a building, not shown, or in an unillustrated air distribution system of a building.
  • the exhaust air AB cooled in the air / air heat exchanger 200 flows out of the air / air heat exchanger 200 as exhaust air FO.
  • the exhaust air is conveyed with an exhaust air fan 251.
  • the exhaust air channel 250 is directed in the exemplary embodiment to the evaporator 160 or connected to the evaporator 160, that the exhaust air FO is passed to the evaporator 160. It is also advantageous to mix the exhaust air FO outside air AU added. In the exemplary embodiment, this outside air AU is mixed by the Venturi principle into the flowing exhaust air FO, and this mixture of exhaust air FO and outside air AU is supplied to the evaporator 160.
  • the gas cooler 170 In normal heating operation, the gas cooler 170 is traversed by air for refrigerant, which from the compressor 110 from a low pressure, in particular from about 20-50 bar in the conduit 185, to a high pressure, in particular of over 73 bar in the supply line 186, is compressed. In the gas cooler 170 for air, heat is transferred from the refrigerant to the supply air ZU. Further, the refrigerant flows through the drain 187 and through the conduit 183 in the flow direction g and b to the refrigerant subcooler 140.
  • the refrigerant is further supercooled by the cold outside air having the outside air temperature T AU and then flows further in the flow direction c to the throttle 150, where is then relaxed and at least then passed in a liquid state in the evaporator 160.
  • the refrigerant is again vaporized and flows in the direction d in the line 185 to the compressor 110.
  • the end of a room supplied supply air ZU advantageous in multiple ways heat is supplied First, in the refrigerant subcooler 140, in particular to ensure here that the air / air heat exchanger 200 does not freeze, secondly in the air / air heat exchanger 200, the air there as outside air AU absorbs heat from the exhaust air AB, and a third heating undergoes the then designated as supply air to former outside air AU in the air heater 230, so that a supply air temperature is provided, which is above the required room temperature.
  • the supply air ZU is further heated by the supply air fan 221, because the energy converted in the supply air fan 221 is not completely absorbed Flow energy implemented. Lossy heat energy is supplied at this point of the supply air fan 221 also as heat of the supply air ZU. However, this so-called fourth air heating is very low in comparison to the three other warming of the supply air.
  • an air heater is shown with which a building with a low heat demand as in a passive house of about 1 - 2 kWh can be heated at an outside temperature of about -10 - -15 ° C.
  • the air heating can advantageously be used for complete heating.
  • the advantage of the invention lies in the fact that it is heated only with air and can be dispensed with a water-filled distribution system. All the heat that is supplied to the building for heating is delivered to the building via the supply air ZU. Therefore, the supply air ZU is heated at an outside temperature of about -10 or -15 ° C to about 50 ° C.
  • exhaust air FU and preferably admixed outside air AU supplied as mixed air to the evaporator 160 With a mixture of exhaust air to outside air results in an outside temperature of about -15 ° C and an exhaust air temperature of about -10 ° C, a slightly above the outside air temperature, which is supplied to the evaporator.
  • the outside air is advantageously already preheated by the refrigerant subcooler 140 and further large amounts of heat are absorbed in the air / air heat exchanger 200.
  • the supply air ZU enters the air heater 230 at a temperature of approx.
  • the evaporator 160 of the heat pump is charged with an air flow, which is additionally generated by an evaporator fan 162.
  • the evaporator fan 162 may in particular also work as exhaust air fan 251 and then promotes exhaust air FO and outside air AU alone, wherein the Exhaust fan omitted.
  • the evaporator fan is arranged in addition to the exhaust air fan.
  • only one exhaust air fan 251 is provided, which, in particular in combination with the opening 161, also at least indirectly sucks in outside air and conveys it to the evaporator.
  • the three-way valve 120 is set so that, starting from the compressor, the refrigerant is passed to the gas cooler 130.
  • the gas cooler 130 arranged in the hot water heat exchanger 330 releases heat to a water flowing in lines 340, 341, 342.
  • the water either directly loads a hot water tank 300 or indirectly - as in the exemplary embodiment - with a arranged in the hot water tank 300 heat exchanger 310.
  • the water is circulated in the lines 340, 341, 342 by a circulation pump 320.
  • the hot water preparation takes place until a set hot water temperature in the hot water tank 300 is reached.
  • FIG. 4 In another embodiment according to Fig. 4 in addition, three further three-way valves are provided, with which a so-called hot gas defrosting of the evaporator 160 takes place.
  • a second three-way valve 121 is still disposed between the compressor 110 and the three-way valve 120.
  • the three-way valve 121 is switched so that the refrigerant is passed directly to the condenser 160. It flows through a third three-way valve 123 directly to the evaporator 160. There, the heat absorbed in the compressor is discharged in the evaporator for defrosting.
  • the refrigerant only flows through the compressor 110, the evaporator 160 and the throttle 150.
  • the refrigerant subcooler 140, the gas cooler 170 for air and the gas cooler 130 for hot water are advantageously not flowed through.
  • the second three-way valve 121 is directed so that the refrigerant flows to the three-way valve 120 and from there via the supply line 186 to the gas cooler 170 for air. From the gas cooler 170 for air, it continues to node 188 and from there to the refrigerant subcooler 140. From the refrigerant subcooler 140, the refrigerant flows to the fourth three-way valve 122, which is set so that the refrigerant flows directly to the throttle 150, is expanded there, and then into the Evaporator 160 flows.
  • the refrigerant flows to the third three-way valve 123, which is set so that the refrigerant flows directly to the compressor 110.
  • the refrigerant flows directly to the compressor 160 because the fourth three-way valve is closed from this direction.
  • the flow directions a, b, c, d, e, f and g indicate the flow direction of the refrigerant in the heating operation.
  • a first cycle q refers to an outdoor temperature of around 10 - 15 ° C at a generally desired room temperature of approx. 20 - 22 ° C.
  • the energy of the refrigerant is 425 kJ / kg at approx. 10 ° C and approx. 45 bar.
  • the refrigerant is compressed to a point q 2 with an enthalpy of approx. 438 kJ / kg at approx. 55 ° C and approx. 80 bar.
  • the refrigerant is passed to the gas cooler 170 for air and gives off here enthalpy, so that the exiting from the gas cooler 170 for air refrigerant approximately an enthalpy of 220 kJ / kg at a point q 3 with about 10 ° C and ca 80 bar.
  • a further subcooling or heat release of the refrigerant takes place towards a point q 3 ', at which the refrigerant has an enthalpy of 200 kJ / kg with about 0 ° C at about 80 bar.
  • the refrigerant subcooler 140 the refrigerant has given up about an enthalpy of about 220 to about 200 kJ / kg to the outside air AU.
  • the refrigerant flows to the throttle 150 and it takes place starting from the point q 3 'an expansion in the idealized state to an enthalpy of about 200 kJ / kg to point q 4 with a pressure of about 436 bar and a temperature of about 0 ° C.
  • the refrigerant continues to the evaporator 160, where it rises from state q 4 back into enthalpy from 200 to 425 kJ / kg at a pressure of about 45 bar and to a temperature of 10 ° C.
  • the refrigerant CO 2 changes to the wet steam state.
  • the second process p which in Fig. 2 is approximately considered an outside temperature of -5 to -15 ° C, especially about -10 ° C.
  • the outside air AU and exhaust air FO is supplied to the evaporator 160 such that the mixing temperature of the mixture of outside air AU and exhaust air FO supplied to the evaporator is slightly above the temperature t AU , in particular at approximately 1-5 ° C.
  • the refrigerant in the evaporator 160 increases Enthalpy up to a value of about 438 kJ / kg or 440 kJ / kg.
  • the refrigerant is compressed from point p 1 at -5 ° C at about 30 bar to the point P 2 at 68 ° C and about 80 bar, whereby a further enthalpy increase to about 475 kJ / kg occurs.
  • the pressure is about 80 bar, whereby the refrigerant is raised from the point p 1 roughly by about 50 bar in pressure.
  • the refrigerant now flows through the gas cooler 170 for air, and the enthalpy is reduced from point p 2 to a point p 3 to about 290 kJ / kg at 30 ° C and about 80 bar.
  • a further reduction to about 275 kJ / kg at about 27 ° C and about 80 bar then takes place in the refrigerant subcooler 140.
  • the refrigerant is thereafter fed to the throttle 150, where it is in the pressure of about 80 bar to about 30 bar at about -5 ° C is reduced.
  • the pressure reduction takes place in an idealized way isenthalp.
  • the refrigerant CO 2 is in the wet steam state.
  • Fig. 3 is exemplified the temperature profile of the refrigerant and the air and in the case of water heating of the water shown.
  • the already preheated in the air / air heat exchanger 200 to about 16 ° C air flows to the air / air heat exchanger, driven by the supply air fan 221, through the gas cooler 170 for air.
  • the supply air fan 221 driven by the supply air fan 221, through the gas cooler 170 for air.
  • an approximately 16 ° C temperature t Ga of the supply air ZU is at an at least partially working in the counterflow gas cooler 170 at this point by the supply air already cooled refrigerant at about 26 ° C from the gas cooler 170 for air leak and into the discharge line 187 at approx. 26 ° C.
  • t kv a possible real course of the temperature over a length I of the gas cooler 170 for air of the refrigerant CO 2
  • t kv a possible real course of the temperature over a length I of the gas cooler 170 for air of the refrigerant CO 2
  • Both temperature curves t k real and t kv show no temperature jumps or abrupt temperature changes. At this temperature drop from about 80 to about 26 ° C loses the refrigerant corresponding enthalpy of about 180 - 300 kJ / kg, corresponding heat is transferred to the air.
  • the temperature profile t L takes place without further jumps. This is also the case when hot water is being produced. But here is the temperature difference lower, at least at the beginning of the hot water, which should start at about 35 ° C, so that a reasonable shower or the like can take place.
  • the hot water should be raised to at least 50 ° C at the temperature t w .
  • the air / air heat exchanger is designed as a cross-countercurrent heat exchanger or countercurrent heat exchanger.
EP12000489.0A 2012-01-26 2012-01-26 Procédé de fonctionnement d'un appareil de chauffage et d'aération et appareil de chauffage et d'aération Active EP2620715B1 (fr)

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EP2620715A1 true EP2620715A1 (fr) 2013-07-31
EP2620715B1 EP2620715B1 (fr) 2014-01-22

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EP (1) EP2620715B1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104456835A (zh) * 2014-10-31 2015-03-25 无锡同方人工环境有限公司 被动房智能控制系统
CN105135588A (zh) * 2015-09-23 2015-12-09 广东美的制冷设备有限公司 换气设备及其控制方法
WO2016151150A1 (fr) * 2015-03-20 2016-09-29 David Sanchez Duque Dispositif de récupération de chaleur
EP3096089A1 (fr) * 2015-04-07 2016-11-23 Ensto Enervent Oy Ab Système permettant de commander le bilan énergétique d'une propriété
DE102017202524A1 (de) * 2017-02-16 2018-08-16 Robert Bosch Gmbh System mit einer Klimatisierungseinrichtung und einer Brauchwassereinrichtung
WO2018185220A3 (fr) * 2017-04-06 2018-12-27 Stiebel Eltron Gmbh & Co.Kg Installation de pompe à chaleur
EP3663657A1 (fr) * 2018-12-07 2020-06-10 Daikin Industries, Ltd. Climatiseur et système de climatisation
WO2020161041A1 (fr) 2019-02-06 2020-08-13 Bas Air Energy Ab Système de ventilation à récupération de chaleur
WO2022017976A1 (fr) * 2020-07-24 2022-01-27 Envola GmbH Système de climatisation d'espaces intérieurs d'un bâtiment
WO2023089138A1 (fr) * 2021-11-19 2023-05-25 Envola GmbH Système de climatisation d'espaces intérieurs d'un bâtiment

Citations (6)

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Publication number Priority date Publication date Assignee Title
EP0960756A1 (fr) * 1998-05-28 1999-12-01 Valeo Climatisation Dispositif de climatisation de véhicule utilisant un fluide réfrigérant à l'état supercritique
DE19702903C2 (de) 1997-01-28 2000-08-24 Stiebel Eltron Gmbh & Co Kg Klimaanlage mit einer Wärmepumpe
DE102005002282A1 (de) 2005-01-18 2006-07-27 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenkreis einer Lüftungsanlage
WO2007080162A2 (fr) * 2006-01-09 2007-07-19 Oxycom Beheer B.V. Dispositif de refroidissement et de ventilation
FR2922632A1 (fr) * 2007-10-18 2009-04-24 Aldes Aeraulique Sa Installation de ventilation mecanique controlee de type double flux thermodynamique reversible
EP2312227A1 (fr) * 2009-09-30 2011-04-20 Aldes Aeraulique Installation de ventilation mécanique contrôlée de type double flux thermodynamique réversible avec production d'eau chaude sanitaire

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19702903C2 (de) 1997-01-28 2000-08-24 Stiebel Eltron Gmbh & Co Kg Klimaanlage mit einer Wärmepumpe
EP0960756A1 (fr) * 1998-05-28 1999-12-01 Valeo Climatisation Dispositif de climatisation de véhicule utilisant un fluide réfrigérant à l'état supercritique
DE102005002282A1 (de) 2005-01-18 2006-07-27 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenkreis einer Lüftungsanlage
WO2007080162A2 (fr) * 2006-01-09 2007-07-19 Oxycom Beheer B.V. Dispositif de refroidissement et de ventilation
FR2922632A1 (fr) * 2007-10-18 2009-04-24 Aldes Aeraulique Sa Installation de ventilation mecanique controlee de type double flux thermodynamique reversible
EP2312227A1 (fr) * 2009-09-30 2011-04-20 Aldes Aeraulique Installation de ventilation mécanique contrôlée de type double flux thermodynamique réversible avec production d'eau chaude sanitaire

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104456835A (zh) * 2014-10-31 2015-03-25 无锡同方人工环境有限公司 被动房智能控制系统
WO2016151150A1 (fr) * 2015-03-20 2016-09-29 David Sanchez Duque Dispositif de récupération de chaleur
EP3096089A1 (fr) * 2015-04-07 2016-11-23 Ensto Enervent Oy Ab Système permettant de commander le bilan énergétique d'une propriété
CN105135588A (zh) * 2015-09-23 2015-12-09 广东美的制冷设备有限公司 换气设备及其控制方法
DE102017202524A1 (de) * 2017-02-16 2018-08-16 Robert Bosch Gmbh System mit einer Klimatisierungseinrichtung und einer Brauchwassereinrichtung
WO2018185220A3 (fr) * 2017-04-06 2018-12-27 Stiebel Eltron Gmbh & Co.Kg Installation de pompe à chaleur
EP3663657A1 (fr) * 2018-12-07 2020-06-10 Daikin Industries, Ltd. Climatiseur et système de climatisation
WO2020161041A1 (fr) 2019-02-06 2020-08-13 Bas Air Energy Ab Système de ventilation à récupération de chaleur
WO2022017976A1 (fr) * 2020-07-24 2022-01-27 Envola GmbH Système de climatisation d'espaces intérieurs d'un bâtiment
WO2023089138A1 (fr) * 2021-11-19 2023-05-25 Envola GmbH Système de climatisation d'espaces intérieurs d'un bâtiment

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